US4421425A - Fixed fad thrust bearing - Google Patents

Fixed fad thrust bearing Download PDF

Info

Publication number
US4421425A
US4421425A US06/379,198 US37919882A US4421425A US 4421425 A US4421425 A US 4421425A US 37919882 A US37919882 A US 37919882A US 4421425 A US4421425 A US 4421425A
Authority
US
United States
Prior art keywords
pad
ring
oil
thrust bearing
cage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US06/379,198
Other languages
English (en)
Inventor
Gerard Foucher
Michel Hermand
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alsthom Atlantique SA
Original Assignee
Alsthom Atlantique SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alsthom Atlantique SA filed Critical Alsthom Atlantique SA
Assigned to SOCIETE ANONYME DITE: ALSTHOM-ATLANTIQUE reassignment SOCIETE ANONYME DITE: ALSTHOM-ATLANTIQUE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: HERMAND, MICHEL, ROUCHER, GERARD
Application granted granted Critical
Publication of US4421425A publication Critical patent/US4421425A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure

Definitions

  • the present invention concerns a fixed pad thrust bearing for a turbomachine.
  • the invention consists in a fixed pad thrust bearing for a turbomachine, comprising a thrust collar integral with a rotor of said turbomachine, a ring comprising two parts of equal size formed with fixed sector-shaped pads separated by radial grooves and disposed around said rotor, deformable means on which a rear surface of said ring bears, a fixed cage containing said ring and said deformable means, oil feed means discharging into said fixed cage, and an annular oil recovery chamber whence oil is evacuated by gravity through one or more passages in the lower part of said fixed cage, wherein each pad is delimited by first and second lateral edges, said first lateral edge being in advance of said second lateral edge in the direction of rotation of said collar, each pad has a front surface facing said collar and an outer edge facing a wall of said cage, each pad has in its front surface an opening adjacent said first lateral edge, which is delimited by first and second inner edges, which does not extend so far as the inner and outer edges of the pad and which is fed by a
  • the advantages of the thrust bearing in accordance with the invention are due to the fact that there is no splashing of the oil in the thrust bearing because the oil is not injected between the fixed and moving parts, at which point the oil has no function, but instead adjacent the first lateral edge of each pad where it has an active role in creating an oil film between the pads and the thrust collar. Furthermore, by virtue of the grooves some of the hot oil, which has accomplished its task, may be evacuated.
  • the thrust bearing comprises sealing means between said outer edges of said pads and said wall of said cage, preventing oil from said oil feed circuit leaking towards said rear surface of said ring or towards said grooves and said front surface of said pads, so limiting oil consumption.
  • said sealing means comprise two thread-like seals surrounding said ring, one on each side of said orifices in said outer edges of said parts.
  • FIG. 1 shows a thrust bearing in accordance with the invention.
  • FIG. 2 is a front view of part of the ring of pads in accordance with the invention.
  • FIG. 3 is a developed cross-section through the ring of pads in FIG. 2, along arcuate line III--III.
  • FIG. 1 is a cross-section through the axis of the thrust bearing in accordance with the invention.
  • the shaft 1 of the turbine comprises a thrust collar 2.
  • the stator of the turbine comprises a thrust bearing cage 3 disposed around collar 2 and containing an elastic ring 4 lining the side of the thrust bearing cage opposite collar 2 and a ring 16 incorporating a number of sector-shaped pads 5 separated by radial grooves 26 formed in said ring 16, extending across the full width of ring 16.
  • stator there is an annular oil feed chamber 6 into which an oil feed line 7 discharges.
  • Passages 8 connect chamber 6 with the inside of thrust-bearing cage 3.
  • a seal 9 is provided between shaft 1 and thrust bearing cage 3 so that oil cannot leak along shaft 1, thereby limiting shear stresses on the oil between shaft 1 and thrust bearing cage 3.
  • annular oil recovery space 10 Oil being evacuated by gravity through one or more passages 11 in the lower part of cage 3.
  • each pad 5 has a first, leading lateral edge 12 and a second trailing lateral edge 13, the latter trailing first lateral edge 12 in the direction of rotation of shaft 1 and collar 2.
  • Grooves 26 are delimited by the second lateral edge 13 of one pad 5 and the first lateral edge 12 of the next following pad 5.
  • Bore 22 feeds oil to a groove 23 machined in front surface 14 and extending along a radius from a point adjacent the outer edge 21 of the pad to a point adjacent the inner edge 24 of the pad, close to first lateral edge 12 of said pad.
  • Groove 23 is delimited by a first, leading inner edge 33 and a second trailing inner edge 34, the latter trailing first inner edge 33 in the direction of rotation of shaft 1 and collar 2.
  • Front surface 14 of each pad 5 faces collar 2 and incorporates a first plane surface 20 parallel to rear surface 15 of ring 16 extending from first lateral edge 12 to inner edge 33.
  • a second plane surface 19 diverges from rear surface 15 of ring 16 in the direction from first inner edge 33 to second lateral edge 13.
  • Rear surface 15 of ring 16 bears on elastic ring 4 via shallow bosses 27 formed on it.
  • pivot pins 17 Fixed to ring 4 are pivot pins 17 each of which penetrates into a cylindrical bore 18 parallel to the axis of the turbomachine in rear surface 15 of ring 16 in line with each pad 5 and preventing rotation of ring 16 relative to elastic ring 4 which is itself keyed against rotation relative to thrust bearing cage 3 by a stop 35.
  • the effect of the oil pressure is to move ring 16 away from collar 2, guided by pivot pins 17 which remain in their respective bores 18.
  • Each passage 8 terminates in a space 28 formed in cage 3 facing orifice 32 of a respective bore 22.
  • a first thread-like seal 29 runs around the ring so as to constitute a torus in the vicinity of rear surface 15 to form a seal between outer edge 21 of pads 5 and the wall of cage 3, to prevent oil leaking from spaces 28 towards rear surface 15.
  • a second thread-like seal 30 runs around ring 6 in the vicinity of the bottoms 31 of grooves 26, forming a seal between outer edge 21 of pads 5 and the wall of cage 3 to prevent oil leaking from spaces 28 towards grooves 26.
  • the cold oil is introduced directly beneath pads 5 without previously being subjected to significant shearing stresses between two surfaces in relative movement, especially in the vicinity of the rotor.
  • the major part of the power consumed by the oil thus contributes to generating the hydrodynamic supporting force.
  • collar 2 could comprise, on the side opposite that shown, a thrust bearing symmetrical so that shown relative to a plane perpendicular to the axis, in which case a common annular space 10 could serve to recover the oil from both bearings.
  • the single groove 23 could be replaced with a series of circular openings disposed along a line in the vicinity of first lateral edge 12.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Supercharger (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US06/379,198 1981-05-15 1982-05-17 Fixed fad thrust bearing Expired - Lifetime US4421425A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8109706A FR2505950A1 (fr) 1981-05-15 1981-05-15 Butee a patins fixes
FR8109706 1981-05-15

Publications (1)

Publication Number Publication Date
US4421425A true US4421425A (en) 1983-12-20

Family

ID=9258498

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/379,198 Expired - Lifetime US4421425A (en) 1981-05-15 1982-05-17 Fixed fad thrust bearing

Country Status (7)

Country Link
US (1) US4421425A (fr)
EP (1) EP0065696B1 (fr)
JP (1) JPS57200720A (fr)
AT (1) ATE17270T1 (fr)
DE (1) DE3268242D1 (fr)
FR (1) FR2505950A1 (fr)
ZA (1) ZA823399B (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722127A1 (de) * 1986-07-10 1988-01-14 Dana Corp Haltering, insbesondere fuer freilaufkupplung
US5626470A (en) * 1996-04-10 1997-05-06 Ingersoll-Rand Company Method for providing lubricant to thrust bearing
US5795076A (en) * 1995-10-13 1998-08-18 Orion Corporation Tilt pad hydrodynamic bearing for rotating machinery
US5879085A (en) * 1995-10-13 1999-03-09 Orion Corporation Tilt pad hydrodynamic bearing for rotating machinery
US5951172A (en) * 1995-10-13 1999-09-14 Orion Corporation Sleeve bearing lubrication
US6024494A (en) * 1998-02-12 2000-02-15 Ingersoll-Dresser Pump Company Polymer-backed thrust bearings
US6460635B1 (en) 1999-10-25 2002-10-08 Kalsi Engineering, Inc. Load responsive hydrodynamic bearing
US20030039417A1 (en) * 2001-06-05 2003-02-27 Aguilar Scott Grover Diverted flow thrust bearing
US20060171616A1 (en) * 2005-02-03 2006-08-03 Kalsi Engineering, Inc. Hydrodynamic thrust bearing assembly
US9109703B2 (en) 2010-02-11 2015-08-18 Kalsi Engineering, Inc. Hydrodynamic backup ring
US9429238B2 (en) 2009-11-30 2016-08-30 Kalsi Engineering, Inc. Dynamic backup ring assembly
US9845879B2 (en) 2009-11-30 2017-12-19 Kalsi Engineering, Inc. High pressure dynamic sealing arrangement
US10330203B2 (en) 2017-01-06 2019-06-25 Kalsi Engineering Inc. High pressure dynamic sealing device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4311117A1 (de) * 1993-04-05 1994-10-06 Abb Management Ag Axiales Gleit-Schublager, insbesondere für Turbolader

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1436265A (en) * 1918-06-03 1922-11-21 Kingsbury Bearing
US2731308A (en) * 1952-08-30 1956-01-17 Gen Electric Self-aligning thrust bearing structure
US3893737A (en) * 1974-04-19 1975-07-08 Marchem Resources Inc Thrust bearing having lubrication system
US3966279A (en) * 1975-06-06 1976-06-29 Westinghouse Electric Corporation High-load capacity, non-tilting thrust bearing
US3982796A (en) * 1973-02-28 1976-09-28 The Glacier Metal Company Limited Thrust bearings
US4277112A (en) * 1979-10-01 1981-07-07 Mechanical Technology Incorporated Stepped, split, cantilevered compliant bearing support

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR484366A (fr) * 1916-02-16 1917-10-02 Charles Algernon Parsons Perfectionnements au graissage de paliers de butée
GB843021A (en) * 1957-09-03 1960-08-04 Napier & Son Ltd Improvements relating to thrust bearings, face seals or the like
GB1392245A (en) * 1971-11-12 1975-04-30 Schwermasch Liebknecht Veb K Axial sliding bearings
JPS5312009B2 (fr) * 1974-02-01 1978-04-26
JPS5945850B2 (ja) * 1979-07-13 1984-11-09 株式会社日立製作所 スラスト軸受

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1436265A (en) * 1918-06-03 1922-11-21 Kingsbury Bearing
US2731308A (en) * 1952-08-30 1956-01-17 Gen Electric Self-aligning thrust bearing structure
US3982796A (en) * 1973-02-28 1976-09-28 The Glacier Metal Company Limited Thrust bearings
US3893737A (en) * 1974-04-19 1975-07-08 Marchem Resources Inc Thrust bearing having lubrication system
US3966279A (en) * 1975-06-06 1976-06-29 Westinghouse Electric Corporation High-load capacity, non-tilting thrust bearing
US4277112A (en) * 1979-10-01 1981-07-07 Mechanical Technology Incorporated Stepped, split, cantilevered compliant bearing support

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722127A1 (de) * 1986-07-10 1988-01-14 Dana Corp Haltering, insbesondere fuer freilaufkupplung
US4757887A (en) * 1986-07-10 1988-07-19 Dana Corporation Split thrust/retainer ring for an overrunning clutch
US5795076A (en) * 1995-10-13 1998-08-18 Orion Corporation Tilt pad hydrodynamic bearing for rotating machinery
US5879085A (en) * 1995-10-13 1999-03-09 Orion Corporation Tilt pad hydrodynamic bearing for rotating machinery
US5951172A (en) * 1995-10-13 1999-09-14 Orion Corporation Sleeve bearing lubrication
US5626470A (en) * 1996-04-10 1997-05-06 Ingersoll-Rand Company Method for providing lubricant to thrust bearing
US6024494A (en) * 1998-02-12 2000-02-15 Ingersoll-Dresser Pump Company Polymer-backed thrust bearings
US6460635B1 (en) 1999-10-25 2002-10-08 Kalsi Engineering, Inc. Load responsive hydrodynamic bearing
US20030039417A1 (en) * 2001-06-05 2003-02-27 Aguilar Scott Grover Diverted flow thrust bearing
US6827494B2 (en) * 2001-06-05 2004-12-07 Honeywell International, Inc. Diverted flow thrust bearing
US20060171616A1 (en) * 2005-02-03 2006-08-03 Kalsi Engineering, Inc. Hydrodynamic thrust bearing assembly
US9429238B2 (en) 2009-11-30 2016-08-30 Kalsi Engineering, Inc. Dynamic backup ring assembly
US9845879B2 (en) 2009-11-30 2017-12-19 Kalsi Engineering, Inc. High pressure dynamic sealing arrangement
US9109703B2 (en) 2010-02-11 2015-08-18 Kalsi Engineering, Inc. Hydrodynamic backup ring
US10330203B2 (en) 2017-01-06 2019-06-25 Kalsi Engineering Inc. High pressure dynamic sealing device

Also Published As

Publication number Publication date
FR2505950A1 (fr) 1982-11-19
ZA823399B (en) 1983-06-29
JPH028165B2 (fr) 1990-02-22
ATE17270T1 (de) 1986-01-15
EP0065696B1 (fr) 1986-01-02
EP0065696A1 (fr) 1982-12-01
DE3268242D1 (en) 1986-02-13
JPS57200720A (en) 1982-12-09
FR2505950B1 (fr) 1985-04-26

Similar Documents

Publication Publication Date Title
US4421425A (en) Fixed fad thrust bearing
US5174584A (en) Fluid bearing face seal for gas turbine engines
EP0163815B1 (fr) Palier de butée
US3390926A (en) Combined journal and thrust bearing
US5271676A (en) Combination package tilt pad journal bearing/dual self equalizing thrust bearings, with hydrostatic lift provisions
EP0361544B1 (fr) Palier
US3708215A (en) Hybrid boost bearing assembly
US5980114A (en) Thrust bearing
EP0081281B1 (fr) Roulement à rouleaux coniques
EP0202702B1 (fr) Etanchéité centrifuge
US3608910A (en) Shaft seal arrangements
US3549215A (en) Hydrostatically supported tilting pad journal bearing
US2870719A (en) Bushing for pressure loaded gear pump having a tapered journal surface
JPH0325613B2 (fr)
GB1421540A (en) Shaft bearing assemblies
US3128713A (en) Hydraulic pump
EP0949428A1 (fr) Palier de butée dynamique du type fermé avec trou traversant
US4927326A (en) Turbomachinery rotor support with damping
JPH07122444B2 (ja) 自給作用を有する流体力学的なラジアルすべり軸受
US5051007A (en) Lubrication of a centrifugal pump bearing
US4822240A (en) Compressor thrust balancer
US3841720A (en) Thrust bearing assembly
CA1299211C (fr) Amelioration de la lubrification de garniture mecanique
US4133541A (en) Seal
JPH09229069A (ja) スラスト軸受装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: SOCIETE ANONYME DITE: ALSTHOM-ATLANTIQUE 38, AVENU

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:ROUCHER, GERARD;HERMAND, MICHEL;REEL/FRAME:004175/0189

Effective date: 19820504

Owner name: SOCIETE ANONYME DITE: ALSTHOM-ATLANTIQUE, FRANCE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ROUCHER, GERARD;HERMAND, MICHEL;REEL/FRAME:004175/0189

Effective date: 19820504

STCF Information on status: patent grant

Free format text: PATENTED CASE

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, PL 96-517 (ORIGINAL EVENT CODE: M170); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 4

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, PL 96-517 (ORIGINAL EVENT CODE: M171); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 8

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 12TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M185); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 12